DE102017116517A1 - Planetary gear train of an automatic transmission for a vehicle - Google Patents

Abstract

A planetary gear train of an automatic transmission for a vehicle is disclosed. The planetary gear train may include: an input shaft (IS) configured to receive torque from an engine, an output shaft (OS) configured to output a torque, a first planetary gear set (PG1) having a first, a second and a third rotary element (N1, N2, N3), a second planetary gear set (PG2) having a fourth, a fifth and a sixth rotary element (N4, N5, N6), a third planetary gear set (PG3), which seventh, eighth and ninth rotary members (N7, N8, N9), a fourth planetary gear set (PG4) having tenth, eleventh and twelfth rotary members (N10, N11, N12), a fifth planetary gear set (PG4), which has a thirteenth, a fourteenth and a fifteenth rotary element (N13, N14, N15). In addition, the planetary gear train has nine shafts (TM1 - TM9) operatively connected to at least one of the rotating members to provide ten forward speeds and one reverse speed, so that more efficient power output and smooth gearshift can be achieved.

Description

Cross-reference to related application

This application claims priority from January 13, 2017 Korean patent application application no. 10-2017-0006059 the entire contents of which are incorporated herein by reference for all purposes.

area

The present invention relates to an automatic transmission for a vehicle which improves the output performance and the fuel economy.

background

The statements in this section merely provide background information related to the present invention and are not necessarily prior art.

In general, an automatic transmission that achieves multiple gear ratios has been developed to increase fuel efficiency and improve drivability.

Such an automatic transmission having a plurality of speed ratios is required to improve drive performance and driving efficiency in engine downsizing. In particular, highly efficient multi-speed transmissions require excellent linearity of step ratios (eg, formed by respective ratios of the lower forward gear ratio divided by the higher forward gear ratio, eg, the first forward gear ratio divided by the second forward gear ratio, etc.) which is closely related to driving characteristics such as acceleration before and after shifting, and a rhythmic engine speed. These properties are considered as properties which ensure competitiveness in the field of automatic transmissions.

However, in the automatic transmission, the number of internal components increases as the number of speed stages increases, and as a result, the mountability, the cost, the weight, the transmission efficiency, and the like may further deteriorate.

Accordingly, the development of a planetary gear train, which may have a small number of components, may be important to increase fuel efficiency.

However, a conventional eight-speed automatic transmission has a gear ratio range, particularly ratio of the first forward gear ratio through the highest forward gear ratio, of 6.5-7.5 (the gear ratio range is an important factor for ensuring the linearity of the Step ratios), and thus an improvement in drive performance and fuel economy can not be great.

In addition, if an eight-speed automatic transmission has a gear ratio range larger than 9.0, it is difficult to ensure the linearity of the step ratios. Thereby, the operating efficiency of an engine and the drivability of a vehicle may be degraded.

The above information disclosed in this Background section is only for enhancement of understanding of the general background of the invention and should not be construed as an admission or any suggestion that this prior art information is familiar to those skilled in the art is, belong.

Explanation of the invention

The present invention / disclosure provides a planetary gear train of a transmission (eg, an automatic transmission, in particular an automatic transmission) for a vehicle, which has the advantages of improving a power output performance (eg, power transmission performance) and fuel efficiency through ten forward speeds and one reverse speed and reducing drag losses of clutches and brakes using five planetary gear sets and six engagement elements.

In addition, with the planetary gear train according to the present invention, a planetary gear train of an automatic transmission for a vehicle is provided which has the advantages of improving a torque transmission efficiency and durability by using a planetary gear set in a torque-parallel manner and by reducing a torque portion of each planetary gear set and each engagement element.

Further, with the planetary gear train according to the present invention, a highly efficient planetary gear train of an automatic transmission for a vehicle is provided which further has the advantages of increasing the flexibility of output transmission ratios and improving the linearity of the step ratios by using has five planetary gear sets to achieve ten forward gear ratios and one reverse gear stage.

A planetary gear train of an automatic transmission for a vehicle (eg, a motor vehicle) according to an exemplary embodiment of the present invention may include: an input shaft (eg, drive shaft) receiving torque from an engine (eg, an engine), an output shaft (eg, output shaft), which torque Outputs a first planetary gear set, which has a fourth, a fifth and a sixth rotary element, a third planetary gear set, which a seventh, a eighth and a ninth rotary member, a fourth planetary gear set having a tenth, an eleventh and a twelfth rotary member, a fifth planetary gear set having a thirteenth, a fourteenth and a fifteenth rotary member, a first shaft connected to the first rotary member and d a second shaft connected to the fourteenth rotary element and the output shaft, a third shaft connected to the sixth rotary element and the thirteenth rotary element, a fourth shaft connected to the eleventh rotary element and the fifteenth rotary element is a fifth shaft which is connected to the fifth rotary member and the eighth rotary member, a sixth shaft which is connected to the ninth rotary member, a seventh shaft which is connected to the third rotary member, the seventh rotary member and the tenth rotary member, an eighth shaft connected to the second rotary element and the fourth rotary element, and a ninth shaft connected to the twelfth rotary element.

In addition, the planetary gear train may further comprise six engagement elements (e.g., shift elements) which selectively connect any shaft of the nine shafts to any other shaft or to a transmission housing, e.g., depending on the shift situation. Each of forward gears or one reverse gear is achieved by operating three (e.g., exactly three) engagement members out of the six engagement members.

In addition, the six engagement members may have three clutches and three brakes, and each of the three clutches is e.g. set up to connect two waves of the nine waves together. Each of the three brakes is e.g. configured to selectively connect the transmission housing to any one of the nine shafts which is not connected to the input shaft or the output shaft.

In addition, the six engagement elements may include: a first clutch disposed between the sixth shaft and the second shaft, a second clutch disposed between the first shaft and the fifth shaft, a third clutch connected between the first shaft and the first shaft third shaft, a first brake disposed between the eighth shaft and the transmission housing, a second brake disposed between the seventh shaft and the transmission housing, and a third brake disposed between the ninth shaft and the transmission housing ,

The six engagement elements may include: a first clutch disposed between the sixth shaft and the fourth shaft, a second clutch disposed between the first shaft and the fifth shaft, a third clutch connected between the first shaft and the third shaft Shaft is arranged, a first brake, which is arranged between the eighth shaft and the transmission housing, a second brake, which is arranged between the seventh shaft and the transmission housing, and a third brake, which is arranged between the ninth shaft and the transmission housing.

In addition, the first, second and third rotary members may respectively be a first sun gear, a first planet carrier and a first ring gear, the fourth, fifth and sixth rotary members may respectively be a second sun gear, a second planet carrier and a second ring gear That is, when the seventh, eighth, and ninth rotary members are respectively associated with a third sun gear, a third planet carrier, and a third ring gear, the tenth, eleventh, and twelfth rotary members may respectively be a fourth sun gear, a fourth planet carrier, and a fourth ring gear , and the thirteenth, fourteenth and fifteenth rotating members may be respectively associated with a fifth sun gear, a fifth planet carrier and a fifth ring gear.

The first, the second, the third, the fourth and the fifth planetary gear set may also from an engine side in an order of the first, the fourth, the third, the second and the fifth planetary gear set (eg from a motor side of the first planetary gear set, then fourth Planetary gear set, then third planetary gear set, then second planetary gear set and then fifth planetary gear set) to be arranged

According to an exemplary embodiment of the present invention, ten forward speeds and one reverse speed can be achieved by combining five planetary gear sets, which are simple planetary gear sets, with six engagement elements.

In addition, since a transmission ratio range of greater than 8.5 is provided, an operating efficiency of the engine can be improved. Further, since the linearity of the step ratios can be provided for a plurality of speed ratios, drivability, such as, e.g. acceleration before and after shifting, the rhythmic engine speed, etc. are improved.

Since ten forward speeds and one reverse speed are achieved using five planetary gear sets, but the number of engagement elements is reduced, drag losses of clutches and brakes can be reduced, and power output efficiency and fuel efficiency can be improved.

In addition, since a planetary gear set is used on an output side in a torque-parallel manner and torque is distributed evenly to each planetary gear set and each engagement element, consequently, the torque output efficiency and the durability can be improved.

Further, since five planetary gear sets are used to achieve ten forward speeds and one reverse speed, the flexibility of output transmission ratios can be increased and linearity of step ratios can be improved.

Other areas of applicability will become apparent from the description provided herein. It should be understood that the description and specific examples are intended for purposes of illustration only and are not intended to limit the scope of the present invention.

list of figures

• 1 eine schematische Darstellung eines Planetengetriebezugs gemäß der ersten Ausführungsform der vorliegenden Erfindung ist,
• 2 ein Beispiel einer Betriebstabelle von Steuerelementen bei jeder Gangstufe in dem Planetengetriebezug gemäß der ersten beispielhaften Ausführungsform der vorliegenden Erfindung ist,
• 3 ein weiteres Beispiel einer Betriebstabelle von Steuerelementen bei jeder Gangstufe in dem Planetengetriebezug gemäß der ersten beispielhaften Ausführungsform der vorliegenden Erfindung ist,
• 4 eine schematische Darstellung eines Planetengetriebezugs gemäß der zweiten Ausführungsform der vorliegenden Erfindung ist,
• 5 ein Beispiel einer Betriebstabelle von Steuerelementen bei jeder Gangstufe in dem Planetengetriebezug gemäß der zweiten beispielhaften Ausführungsform der vorliegenden Erfindung ist, und
• 6 ein weiteres Beispiel einer Betriebstabelle von Steuerelementen bei jeder Gangstufe in dem Planetengetriebezug gemäß der zweiten beispielhaften Ausführungsform der vorliegenden Erfindung ist.

In order that the invention may be well understood, numerous embodiments thereof, given by way of example, will now be described, with reference to the accompanying drawings, in which:

• 1 FIG. 2 is a schematic diagram of a planetary gear train according to the first embodiment of the present invention; FIG.
• 2 an example of an operation table of controls at each gear stage in the planetary gear train according to the first exemplary embodiment of the present invention;
• 3 another example of an operation table of controls at each gear stage in the planetary gear train according to the first exemplary embodiment of the present invention;
• 4 FIG. 3 is a schematic diagram of a planetary gear train according to the second embodiment of the present invention; FIG.
• 5 an example of an operation table of controls at each gear stage in the planetary gear train according to the second exemplary embodiment of the present invention, and
• 6 Another example of an operation table of controls at each gear stage in the planetary gear train according to the second exemplary embodiment of the present invention.

The drawings described herein are for illustration purposes only and are not intended to limit the scope of the present invention in any way.

Detailed description

The following description is merely exemplary in nature and is not intended to limit the present invention, application, or use. It should be understood that throughout the drawings, corresponding reference numerals indicate like or corresponding parts and features.

Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to the accompanying drawings.

However, descriptions of parts which are not in connection with the description of the invention are omitted for a clear description of the exemplary embodiments of the present invention.

In the following description, dividing names of components into "first", "second" and the like is to distinguish the names because the names of the components are equal to each other, and in particular, their order is not limited. In this application, the terms "wheel" and "wheels" also include a "gear" as well as "gears" in general. If this is referred to by an engagement between wheels of a transmission, so this intervention, for example, by be implemented a meshing between the gears designed as gears of the transmission.

1 FIG. 12 is a schematic diagram of a planetary gear train according to the first exemplary embodiment of the present invention. FIG.

Regarding 1 comprises a planetary gear train (eg a planetary gear device): a first, a second, a third, a fourth and a fifth planetary gear set (or planetary gear set) PG1 . PG2 . PG3 , PG4 and PG5 which are arranged on the same axis, an input shaft (eg drive shaft) IS , an output shaft (eg output shaft) OS , nine waves TM1 to TM9, which is provided with at least one rotary element of the first, the second, the third, the fourth and the fifth planetary gear set (ie PG1 . PG2 . PG3 . PG4 and PG5 ), engagement elements, which three clutches C1 to C3 and three brakes B1 to B3 and a transmission housing H.

A torque input from an engine (eg, an engine) to the input shaft IS is made by cooperation of the first, second, third, fourth, and fifth planetary gear sets PG1 . PG2 . PG3 . PG4 and PG5 changed, and the changed torque is transmitted through the output shaft OS issued.

According to the first exemplary embodiment of the present invention, the planetary gear sets are from the engine in an order of the first, the fourth, the third, the second and the fifth planetary gear set PG1 . PG4 , PG3, PG2 and PG5 arranged (eg follows from the engine to the first planetary gear set PG1 the fourth planetary gear set PG4 , then the third planetary gear set PG3 , then the second planetary gear set PG2 and finally the fifth planetary gear set PG5 ).

The input shaft IS is an input element, and torque from a crankshaft of the engine is torque converted by a torque converter to enter the input shaft IS to be entered.

The output shaft OS is an output element that is together with the input shaft IS arranged on the same axis and transmits a drive torque via a differential device (eg, a differential gear) to a traction drive.

The first planetary gear set PG1 is a single planetary gear set (also called a planetary gear set with single planet wheels) and includes: a first sun gear S1 , which is a first rotary element N1, a first planet carrier PC1 which is a second rotary element N2 and which at least one first planetary gear P1, which with the first sun gear S1 of the first rotary element N1 is engaged, rotatably supported, and a first ring gear R1 which is a third rotary element N3 and is engaged with the first planetary gear P1.

The second planetary gear set PG2 is a single planetary gear set and includes: a second sun gear S2 , which is a fourth rotary element N4, a second planet carrier PC2 , which is a fifth rotary element N5 and which at least one second planetary gear P2, which is connected to the second sun gear S2 of the fourth rotary element N4 is rotatably supported, and a second ring gear R2 which is a sixth rotary element N6 and is engaged with the second planetary gear P2.

The third planetary gear set PG3 is a single planetary gear set and includes: a third sun gear S3 , which is a seventh rotary element N7, a third planet carrier PC3 which is an eighth rotary element N8 and which at least a third planetary gear P3, which with the third sun gear S3 of the seventh rotary element N7 is engaged, rotatably supported, and a third ring gear R3 which is a ninth rotary element N9 and is engaged with the third planetary gear P3.

The fourth planetary gear set PG4 is a single planetary gear set and includes: a fourth sun gear S4 , which is a tenth rotary element N10, a fourth planet carrier PC4 , which is an eleventh rotary element N11 and which at least one fourth planetary gear P4, which with the fourth sun gear S4 of the tenth rotary element N10 is rotatably supported, and a fourth ring gear R4 which is a twelfth rotary element N12 and is engaged with the fourth planetary gear P4.

The fifth planetary gear set PG5 is a single planetary gear set and includes: a fifth sun gear S5 , which is a thirteenth rotary element N13, a fifth planet carrier PC5 , which is a fourteenth rotary element N14 and which at least one fifth planetary gear P5, which with the fifth sun gear S5 of the thirteenth rotary element N13 is engaged, rotatably supported, and a fifth ring gear R5 which is a fifteenth rotary element N15 and is engaged with the fifth planetary gear P5.

The second rotary element N2 is directly connected to the fourth rotary element N4, the third rotary element N3 is directly connected to the seventh rotary element N7 and the tenth rotary element N10 the fifth rotary element N5 is directly connected to the eighth rotary element N8, the sixth rotary element N6 is directly connected to the thirteenth rotary element N13, and the eleventh rotary element N11 is directly connected to the fifteenth rotary element N15, so that the first, the second, the third, fourth and fifth planetary gear sets PG1 . PG2 . PG3 . PG4 and PG5 with nine waves TM1 to TM9 operate.

The nine waves TM1 to TM9 will be further described in detail.

The nine waves TM1 to TM9 can rotate elements of the rotary elements of the planetary gear set PG1 . PG2 . PG3 . PG4 and PG5 connect directly with each other. The nine waves TM1 to TM9 For example, rotation parts connected to any rotary member and rotating with the rotary member to transmit torque may be rotary members selectively connecting any rotary member to the transmission housing H, for example, depending on the shift situation. The nine waves TM1 to TM9 (For example, one or more of the nine waves) may be, for example, in one embodiment, fixed elements that connect any rotary element with the transmission housing H directly.

The first wave TM1 is directly with the first rotary element N1 (first sun gear S1 ) and is directly connected to the input shaft IS connected so that it is always operated as an input element.

The second wave TM2 is directly with the fourteenth rotary element N14 (fifth planet carrier PC5 ) and is directly connected to the output shaft OS connected so that it is always operated as an output element.

The third wave TM3 is connected to the sixth rotary element N6 (second ring gear R2) and to the thirteenth rotary element N13 (fifth sun gear S5 ) directly connected.

The fourth wave TM4 is with the eleventh rotary element N11 (fourth planet carrier PC4 ) and the fifteenth rotary element N15 (fifth ring gear R5 ) directly connected.

The fifth wave TM5 is with the fifth rotary element N5 (second planet carrier PC2 ) and the eighth rotary element N8 (third planet carrier PC3) directly connected.

The sixth wave TM6 is directly connected to the ninth rotary element N9 (third ring gear R3).

The seventh wave TM7 is with the third rotary element N3 (first ring gear R1 ), the seventh rotary element N7 (third sun gear S3 ) and the tenth rotary element N10 (fourth sun gear S4 ) directly connected.

The eighth wave TM8 is with the second rotary element N2 (first planet carrier PC1 ) and the fourth rotary element N4 (second sun gear S2 ) directly connected.

The ninth wave TM9 is directly connected to the twelfth rotary element N12 (fourth ring gear R4).

The second wave TM2 is here with the sixth wave TM6 selectively connected, and each of the third wave TM3 and the fifth wave TM5 is selectively connected to the first shaft TM1 to operate as a selective input element.

Besides, each is from the seventh wave TM7 , the eighth wave TM9 and the ninth wave TM9 is selectively connected to the transmission housing H to operate as a selective (or selected) fixed member (eg, selected fixing member).

Three couplings C1 . C2 and C3 which are engagement elements are at portions where any two waves of the nine waves TM1 to TM9 as well as from the input shaft IS and the output shaft OS are selectively interconnected.

There are also three brakes B1 . B2 and B3 which are engagement elements, at portions where any wave from the nine waves TM1 to TM9 is selectively connected to the transmission housing H arranged.

An arrangement of the six engagement elements (three clutches C1 to C3 and three brakes B1 to B3 ) will be described in detail.

The first clutch C1 is between the second wave TM2 and the sixth wave TM6 arranged and selectively connects the second wave TM2 with the sixth wave TM6 ,

The second clutch C2 is between the first wave TM1 and the fifth wave TM5 arranged and selectively connects the first wave TM1 with the fifth wave TM5.

The third clutch C3 is between the first wave TM1 and the third wave TM3 arranged and selectively connects the first wave TM1 with the third wave TM3.

The first brake B1 is between the eighth wave TM8 and the transmission housing H and selectively connects the eighth shaft TM8 with the transmission housing H.

The second brake B2 is between the seventh wave TM7 and the transmission housing H, and selectively connects the seventh shaft TM7 with the transmission housing H.

The third brake B3 is between the ninth wave TM9 and the transmission housing H, and selectively connects the ninth shaft TM9 with the transmission housing H.

With reference to 1 is shown that the second clutch C2 and the third clutch C3 appropriately assigned the fifth wave TM5 or the third wave TM3 with the first wave TM1 connect selectively (eg is the fifth wave TM5 over the second clutch C2 with the first wave TM1 connectable and is the third wave TM3 over the third clutch C3 with the first wave TM1 connectable). Because the first wave TM1 directly to the input shaft IS connected, the second clutch C2 be adapted to the input shaft IS with the fifth wave TM5 selectively connect, and can be the third clutch C3 be adapted to the input shaft IS with the third wave TM3 selectively connect.

The engagement elements including the first, second, and third clutches (ie, C1, C2, and C3) and the first, second, and third brakes (ie, B1, B2, and B3) may be wet-type multi-plate friction elements be operated by hydraulic pressure.

2 FIG. 10 is an example of an operation table of controls at each gear stage in the planetary gear train of the first exemplary embodiment of the present invention. FIG.

Referring to 2 become three engagement elements among the first, the second and the third clutch C1 . C2 and C3 and the first, second and third brakes B1 . B2 and B3 operated at each gear stage in the planetary gear train (in other words, from the set of engagement elements, which are the three clutches C1 . C2 and C3 as well as the three brakes B1 . B2 and B3 has three specific engagement elements operated at each gear stage in the planetary gear train).

The first clutch C2 and the first and third brakes B1 and B3 are operated simultaneously in a first forward gear D1.

In a state in which by operation (hereinafter: "operation") of the third clutch C3 the first wave TM1 with the third wave TM3 is connected, torque is the input shaft IS in the first wave TM1 and in the third wave TM3 entered (or introduced). In addition, by operating the first and third brakes B1 and B3 the eighth wave TM8 and the ninth wave TM9 operated as the fixed elements. This will increase the torque of the input shaft IS switched to the first forward speed (eg converted), and the first forward speed is through the output shaft OS , which with the second wave TM2 connected, issued.

The third clutch C3 and the second and third brakes B2 and B3 are operated simultaneously in a second forward gear D2

In a state in which by operation of the third clutch C3 the first wave TM1 with the third wave TM3 is connected, the torque of the input shaft IS in the first wave TM1 and in the third wave TM3 entered. In addition, by operating the second and third brakes B2 and B3 the seventh wave TM7 and the ninth wave TM9 operated as the fixed elements. This will increase the torque of the input shaft IS switched to the second forward speed (eg converted), and the second forward speed is through the output shaft OS , which with the second wave TM2 connected, issued.

The second clutch C2 and the second and third brakes B2 and B3 are operated simultaneously in a third forward gear D3

In a state in which by operation of the second clutch C2 the first wave TM1 with the fifth wave TM5 is connected, the torque of the input shaft IS in the first wave TM1 and in the fifth wave TM5 entered. In addition, by operating the second and third brakes B2 and B3 the seventh wave TM7 and the ninth wave TM9 operated as the fixed elements. This will increase the torque of the input shaft IS switched to the third forward speed (eg converted), and the third forward speed is through the output shaft OS , which with the second wave TM2 connected, issued.

The second and the third clutch C2 and C3 as well as the third brake B3 are operated simultaneously in a fourth forward gear D4

In a state in which the first wave TM1 by operation of the second clutch C2 with the fifth wave TM5 connected and the first wave TM1 by operation of the third clutch C3 with the third wave TM3 is connected, the torque of the input shaft IS in the first wave TM1 , the fifth wave TM5 and the third wave TM3 entered. In addition, by operating the third brake B3 the ninth wave TM9 operated as the fixed element. This will increase the torque of the input shaft IS switched to the fourth forward speed (eg converted), and the fourth forward speed is through the output shaft OS , which with the second wave TM2 connected, issued.

The first and the second clutch C1 and C2 as well as the third brake B3 are operated simultaneously in a fifth forward gear D5

In a state in which the second wave TM2 by operation of the first clutch C1 with the sixth wave TM6 connected and the first wave TM1 by operation of the second clutch C2 with the fifth wave TM5 is connected, the torque of the input shaft IS in the first wave TM1 and in the fifth wave TM5 entered. In addition, by the operation of the third brake B3 the ninth wave TM9 operated as the fixed element. This will increase the torque of the input shaft IS switched to the fifth forward speed (eg converted), and the fifth forward speed is through the output shaft OS , which with the second wave TM2 connected, issued.

The first and the third clutch C1 and C3 as well as the third brake B3 are operated simultaneously in a sixth forward gear D6

In a state in which the second wave TM2 by operation of the first clutch C1 with the sixth wave TM6 connected and the first wave TM1 by operation of the third clutch C3 with the third wave TM3 is connected, the torque of the input shaft IS in the first wave TM1 and in the third wave TM3 entered. In addition, by operating the third brake B3 the ninth wave TM9 operated as the fixed element. This will increase the torque of the input shaft IS switched to the sixth forward speed (eg converted), and the sixth forward speed is through the output shaft OS , which with the second wave TM2 connected, issued.

The first, the second and the third clutch C1 . C2 and C3 are operated simultaneously in a seventh forward gear D7

If the second wave TM2 by operation of the first clutch C1 with the sixth wave TM6 connected, the first wave TM1 by operation of the second clutch C2 with the fifth wave TM5 connected and the first wave TM1 by operation of the third clutch C3 with the third wave TM3 For example, a direct ratio or 1: 1 ratio is generated by a rotation of all parts (sun gear, planet carrier, ring gear) of each planetary gear set at the same speed as a block (block circulation)). If in this state, the torque of the input shaft IS in the first wave TM1 , the fifth wave TM5 and the third wave TM3 is input, the torque of the input shaft IS does not change and becomes the seventh forward gear through the output shaft OS , which with the second wave TM2 connected, issued.

The first and the third clutch C1 and C3 as well as the second brake B2 are operated simultaneously in an eighth forward gear D8.

In a state in which the second wave TM2 by operation of the first clutch C1 with the sixth wave TM6 connected and the first wave TM1 by operation of the third clutch C3 with the third wave TM3 is connected, the torque of the input shaft IS in the first wave TM1 and in the third wave TM3 entered. In addition, by operation of the second brake B2 the seventh wave TM7 operated as the fixed element. This will increase the torque of the input shaft IS switched to the eighth forward speed (eg converted), and the eighth forward speed is through the output shaft OS , which with the second wave TM2 connected, issued.

The first and the second clutch C1 and C2 as well as the second brake B2 are operated simultaneously in a ninth forward gear D9.

In a state in which the second wave TM2 by operation of the first clutch C1 with the sixth wave TM6 connected and the first wave TM1 by operation of the second clutch C2 with the fifth wave TM5 is connected, the torque of the input shaft IS in the first wave TM1 and in the fifth wave TM5 entered. In addition, by operation of the second brake B2 the seventh wave TM7 operated as the fixed element. This will increase the torque of the input shaft IS switched to the ninth forward speed (eg converted), and the ninth forward speed is through the output shaft OS , which with the second wave TM2 connected, issued.

The first and the second clutch C1 and C2 as well as the first brake B1 are operated simultaneously in a tenth forward gear D10.

In a state in which the second wave TM2 by operation of the first clutch C1 with the sixth wave TM6 is connected and the first wave TM1 by operation of the second clutch C2 with the fifth wave TM5 is connected, the torque of the input shaft IS in the first wave TM1 and in the fifth wave TM5 entered. In addition, by operation of the first brake B1 the eighth wave TM8 operated as the fixed element. This will increase the torque of the input shaft IS switched to the tenth forward gear (eg converted), and the tenth forward gear is through the output shaft OS , which with the second wave TM2 connected, issued.

The first clutch C1 and the first and third brakes B1 and B3 are operated simultaneously in a reverse gear REV.

In a state in which the second wave TM2 by operation of the first clutch C1 with the sixth wave TM6 is connected, the torque of the input shaft IS in the first wave TM1 entered. In addition, by operating the first and third brakes B1 and B3 the eighth wave TM8 and the ninth wave TM9 operated as the fixed elements. This will increase the torque of the input shaft IS switched to the reverse gear (eg converted), and the reverse gear is through the output shaft OS , which is connected to the second shaft TM2, output at a reverse rotational speed.

3 FIG. 12 is another example of an operation table of controls at each gear stage in the planetary gear train according to the first exemplary embodiment of the present invention. FIG.

With reference to 3 shows the other example of the operation table that engagement elements in the second forward speed D2 of those in the in 2 shown example are different.

That means referring to 3 in the second forward gear D2, the second clutch C2 and the first and third brakes B1 and B3 be operated simultaneously.

In a state in which by operation of the second clutch C2 the first wave TM1 with the fifth wave TM5 is connected, the torque of the input shaft IS in the first wave TM1 and in the fifth wave TM5 entered. In addition, by operating the first and third brakes B1 and B3 the eighth wave TM8 and the ninth wave TM9 operated as the fixed elements. This will increase the torque of the input shaft IS switched to the second forward speed (eg converted), and the second forward speed is through the output shaft OS , which with the second wave TM2 connected, issued.

A gear ratio of each gear ratio, step ratios, and a gear ratio range may be described with reference to FIGS 2 and 3 shown operating tables are set appropriately.

4 is a schematic representation of a planetary gear train according to the second embodiment of the present invention.

With particular reference to 1 and 4 is the first clutch in the planetary gear train according to the first exemplary embodiment of the present invention C1 between the second wave TM2 and the sixth wave TM6 arranged and connects these selectively the second wave TM2 with the sixth wave TM6 whereas in the planetary gear train according to the second exemplary embodiment of the present invention, the first clutch C1 between the fourth wave TM4 and the sixth wave TM6 is arranged and the fourth wave TM4 with the sixth wave TM6 selectively connects.

Nine waves TM1 to TM9 , Arrangements of two couplings C2 and C3 and three brakes B1 to B3 , Functions and operations of the second exemplary embodiment are except for the first clutch C1 , the same as those of the first exemplary embodiment.

5 and 6 FIG. 14 are two examples of an operation table of controls at each gear stage in the planetary gear train according to the second exemplary embodiment of the present invention.

In the 5 and 6 The operation tables shown are respectively the same as those shown in FIG 2 or in 3 are shown (with the exception of realized gear ratios).

Because the arrangement of the first clutch C1 According to the second exemplary embodiment of the present invention, unlike that according to the first exemplary embodiment of the present invention, the gear ratio of each gear ratio, step ratios, and a gear ratio range can be described with reference to FIGS 5 and 6 shown operating tables are set appropriately.

According to the first and second exemplary embodiments of the present invention, ten forward speeds and one reverse speed can be achieved by having five forward speeds Planetary gear sets PG1 . PG2 . PG3 . PG4 and PG5 and six engagement elements, which three clutch C1 . C2 and C3 and three brakes B1 , B2 and B3 are used.

In addition, since a gear ratio range of greater than 8.5 can be secured, an operating efficiency of the engine can be improved. Furthermore, since the linearity of the step ratios can be ensured due to multiple gear ratios, the drivability, such as, e.g. acceleration before and after shifting, the rhythmic engine speed, etc. are improved.

Further, since ten forward speeds and one reverse speed are achieved by using a reduced number of engagement elements, drag losses of clutches and brakes can be reduced, and power output efficiency and fuel efficiency can be improved.

In addition, since an output-side planetary gear set is used in a torque-parallel manner and torque is uniformly distributed to each planetary gear set and each engagement element, the torque-output efficiency and the durability can be improved.

Further, since five planetary gear sets are used to achieve ten forward speeds and one reverse speed, the flexibility of output transmission ratios can be increased and linearity of step ratios can be improved.

Although the exemplary embodiment of the present invention has been disclosed for illustrative purposes, those skilled in the art will appreciate that numerous modifications, additions and substitutions are possible, without departing from the scope of the invention as described in the appended claims.

LIST OF REFERENCE NUMBERS

PG1, PG2, PG3, PG4, PG5:

first, second, third, fourth and fifth planetary gear set

S1, S2, S3, S4, S5:

first, second, third, fourth and fifth sun wheel

PC1, PC2, PC3, PC4, PC5:

first, second, third, fourth and fifth planet carrier

R1, R2, R3, R4, R5:

first, second, third, fourth and fifth ring gears

C1, C2, C3:

first, second and third clutch

B1, B2, B3:

first, second and third brake

IS:

input shaft

OS:

output shaft

TM1, TM2, TM3, TM4, TM5, TM6, TM7, TM8, TM9:

first, second, third, fourth, fifth, sixth, seventh, eighth and ninth wave

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• KR 1020170006059 [0001]

Claims (20)

Planetary gear train of an automatic transmission for a vehicle, wherein the planetary gear train comprises: an input shaft (IS) configured to receive torque from an engine, an output shaft (OS) adapted to output a changed torque, a first planetary gear set (PG1) having a first, a second and a third rotary element (N1, N2, N3), a second planetary gear set (PG2) having a fourth, a fifth and a sixth rotary element (N4, N5, N6), a third planetary gear set (PG3) having a seventh, an eighth and a ninth rotary element (N7, N8, N9), a fourth planetary gear set (PG4) having a tenth, an eleventh and a twelfth rotary element (N10, N11, N12), a fifth planetary gear set (PG4) having a thirteenth, a fourteenth and a fifteenth rotary element (N13, N14, N15), a first shaft (TM1) connected to the first rotary element (N1) and the input shaft (IS), a second shaft (TM2) connected to the fourteenth rotary element (N14) and the output shaft (OS), a third shaft (TM3) connected to the sixth rotary element (N6) and the thirteenth rotary element (N13), a fourth shaft (TM4) connected to the eleventh rotary element (N11) and the fifteenth rotary element (N15), a fifth shaft (TM5) connected to the fifth rotary element (N5) and the eighth rotary element (N8), a sixth shaft (TM6) connected to the ninth rotary element (N9), a seventh shaft (TM7) connected to the third rotary element (N3), the seventh rotary element (N7) and the tenth rotary element (N10), an eighth shaft (TM8) connected to the second rotary element (N2) and the fourth rotary element (N4), and a ninth wave (TM9) connected to the twelfth rotary element (N12). Planetary gear train according to Claim 1 , further comprising six engaging elements (C1, C2, C3, B1, B2, B3) adapted to rotate one of the nine shafts (TM1 - TM9) with a transmission housing (H) or with another of the nine shafts (TM1 - TM9) selectively, each of forward gears or one reverse gear being achieved by operating three engagement elements of the six engagement elements (C1, C2, C3, B1, B2, B3). Planetary gear train according to Claim 2 wherein the six engagement elements (C1, C2, C3, B1, B2, B3) have three clutches (C1, C2, C3) and three brakes (B1, B2, B3), and wherein each of the three clutches (C1, C2 , C3) is adapted to connect two shafts of the nine shafts (TM1 - TM9) together, and each of the three brakes (B1, B2, B3) is adapted to the transmission housing (H) with any of the nine Waves (TM1 - TM9), which is not connected to the input shaft (IS) or the output shaft (OS) to connect selectively. Planetary gear train according to Claim 2 or 3 wherein the six engagement elements (C1, C2, C3, B1, B2, B3) comprise: a first clutch (C1) arranged between the sixth shaft (TM6) and the second shaft (TM2), a second clutch (C2 ) disposed between the first shaft (TM1) and the fifth shaft (TM5), a third clutch (C3) interposed between the first shaft (TM1) and the third shaft (TM3), a first brake (B1 ) disposed between the eighth shaft (TM8) and the transmission case (H), a second brake (B2) interposed between the seventh shaft (TM7) and the transmission case (H), and a third brake (B3) which is disposed between the ninth shaft (TM9) and the transmission case (H). Planetary gear train according to Claim 2 or 3 wherein the six engagement elements (C1, C2, C3, B1, B2, B3) comprise: a first clutch (C1) arranged between the sixth shaft (TM6) and the fourth shaft (TM4), a second clutch (C2 ) disposed between the first shaft (TM1) and the fifth shaft (TM5), a third clutch (C3) interposed between the first shaft (TM1) and the third shaft (TM3), a first brake (B1 ) disposed between the eighth shaft (TM8) and the transmission case (H), a second brake (B2) interposed between the seventh shaft (TM7) and the transmission case (H), and a third brake (B3) which is disposed between the ninth shaft (TM9) and the transmission case (H). Planetary gear train according to any one of Claims 1 to 5 wherein the first, second and third rotary elements (N1, N2, N3) respectively associated with a first sun gear (S1), a first planet carrier (PC1) and a first ring gear (R1), the fourth, the fifth and the sixth rotary element (N4, N5, N6) respectively associated with a second sun gear (S2), a second Planet carrier (PC2) and a second ring gear (R2), the seventh, the eighth and the ninth rotary member (N7, N8, N9) respectively associated with a third sun gear (S3), a third planet carrier (PC3) and a third ring gear (R3 ), the tenth, eleventh, and twelfth rotary elements (N10, N11, N12) are respectively associated with a fourth sun gear (S4), a fourth planet carrier (PC4), and a fourth ring gear (R4), and the thirteenth, fourteenth, and the fifteenth rotary element (N13, N14, N15) respectively associated with a fifth sun gear (S5), a fifth planet carrier (PC5) and a fifth ring gear (R5) are. Planetary gear train according to any one of Claims 1 to 6 wherein the first, second, third, fourth and fifth planetary gear sets (PG1, PG2, PG3, PG4, PG5) from an engine side in an order of the first, fourth, third, second and fifth planetary gear sets (PG1, PG4, PG3, PG2, PG5) are arranged. Planetary gear train of an automatic transmission for a vehicle, wherein the planetary gear train comprises: an input shaft (IS) configured to receive torque from an engine, an output shaft (OS) configured to output a torque a first planetary gear set (PG1) having a first, a second and a third rotary element (N1, N2, N3), a second planetary gear set (PG2) having a fourth, a fifth and a sixth rotary element (N4, N5, N6), a third planetary gear set (PG3) having a seventh, an eighth and a ninth rotary element (N7, N8, N9), a fourth planetary gear set (PG4) having a tenth, an eleventh and a twelfth rotary element (N10, N11, N12), a fifth planetary gear set (PG4) having a thirteenth, a fourteenth and a fifteenth rotary element (N13, N14, N15), a first shaft (TM1) connected to the first rotary element (N1) and the input shaft (IS), a second shaft (TM2) connected to the fourteenth rotary element (N14) and the output shaft (OS), a third shaft (TM3) connected to the sixth rotary element (N6) and the thirteenth rotary element (N13), a fourth shaft (TM4) connected to the eleventh rotary element (N11) and the fifteenth rotary element (N15), a fifth shaft (TM5) connected to the fifth rotary element (N5) and the eighth rotary element (N8), a sixth shaft (TM6) connected to the ninth rotary element (N9), and a plurality of shafts (TM7 - TM9), each of which is adapted to a transmission housing (H) with any of or a combination of other, not connected to another rotary element rotary elements of the first, the second, the third and the fourth planetary gear set (PG1, PG2, PG3, PG4) selectively connect. Planetary gear train according to Claim 8 wherein the plurality of shafts (TM7 - TM9) comprises: a seventh shaft (TM7) connected to the third rotary element (N3), the seventh rotary element (N7) and the tenth rotary element (N10), an eighth shaft (TM8 ) connected to the second rotary element (N2) and the fourth rotary element (N4), and a ninth wave (TM9) connected to the twelfth rotary element (N12). Planetary gear train according to Claim 9 , further comprising: three clutches (C1, C2, C3) each configured to connect two waves of the nine waves (TM1 - TM9) and three brakes (B1, B2, B3), each of which is arranged to selectively connect the gear housing (H) with another shaft of the nine shafts (TM1 - TM9) which is not connected to the input shaft (IS) or the output shaft (OS). Planetary gear train according to Claim 10 , wherein the three clutches (C1, C2, C3) comprise: a first clutch (C1) arranged between the sixth shaft (TM6) and the second shaft (TM2); a second clutch (C2) arranged between the first A third clutch (C3) which is arranged between the first shaft (TM1) and the third shaft (TM3), and wherein the three brakes (B1, B2, B3 ): a first brake (B1) disposed between the eighth shaft (TM8) and the transmission case (H), a second brake (B2) disposed between the seventh shaft (TM7) and the transmission case (H) and a third brake (B3) interposed between the ninth shaft (TM9) and the transmission case (H). Planetary gear train according to Claim 10 , wherein the three clutches (C1, C2, C3) comprise: a first clutch (C1) arranged between the sixth shaft (TM6) and the fourth shaft (TM4); a second clutch (C2) arranged between the first A third clutch (C3) which is arranged between the first shaft (TM1) and the third shaft (TM3), and wherein the three brakes (B1, B2, B3 ): a first brake (B1) disposed between the eighth shaft (TM8) and the transmission case (H), a second brake (B2) disposed between the seventh shaft (TM7) and the transmission case (H) , and a third brake (B3) interposed between the ninth shaft (TM9) and the transmission case (H). Planetary gear train according to any one of Claims 8 to 12 wherein the first, second and third rotary members (N1, N2, N3) are respectively associated with a first sun gear (S1), a first planet carrier (PC1) and a first ring gear (R1), the fourth, the fifth and the sixth Rotary element (N4, N5, N6) respectively associated with a second sun gear (S2), a second planet carrier (PC2) and a second ring gear (R2), the seventh, the eighth and the ninth rotary element (N7, N8, N9) respectively assigned a third sun gear (S3), a third planet carrier (PC3) and a third ring gear (R3), the tenth, eleventh and twelfth rotational elements (N10, N11, N12) are respectively associated with a fourth sun gear (S4), a fourth planet carrier (PC4) and a fourth ring gear (R4), and the thirteenth, fourteenth and fifteenth rotational elements (N13, N14, N15) are respectively associated with a fifth sun gear (S5), a fifth planet carrier (PC5) and a fifth ring gear (R5 ) are. Planetary gear train according to any one of Claims 8 to 13 wherein the first, second, third, fourth and fifth planetary gear sets (PG1, PG2, PG3, PG4, PG5) from an engine side in an order of the first, fourth, third, second and fifth planetary gear sets (PG1, PG4, PG3, PG2, PG5) are arranged. Planetary gear train of an automatic transmission for a vehicle, wherein the planetary gear train comprises: an input shaft (IS) configured to receive torque from an engine, an output shaft (OS) configured to output a torque a first planetary gear set (PG1) having a first, a second and a third rotary element (N1, N2, N3), a second planetary gear set (PG2) having a fourth, a fifth and a sixth rotary element (N4, N5, N6), a third planetary gear set (PG3) having a seventh, an eighth and a ninth rotary element (N7, N8, N9), a fourth planetary gear set (PG4) having a tenth, an eleventh and a twelfth rotary element (N10, N11, N12), a fifth planetary gear set (PG4) having a thirteenth, a fourteenth and a fifteenth rotary element (N13, N14, N15), a first shaft (TM1) connected to the first rotary element (N1) and the input shaft (IS), a second shaft (TM2) connected to the fourteenth rotary element (N14) and the output shaft (OS), a third shaft (TM3) connected to the sixth rotary element (N6) and the thirteenth rotary element (N13), a fourth shaft (TM4) connected to the eleventh rotary element (N11) and the fifteenth rotary element (N15), a fifth shaft (TM5) connected to the fifth rotary element (N5) and the eighth rotary element (N8), a sixth shaft (TM6) connected to the ninth rotary element (N9) and selectively connected to one of the second shaft (TM2) and the fourth shaft (TM4), a seventh wave (TM7), an eighth wave (TM8) and a ninth wave (TM9), wherein each of the seventh shaft (TM7), the eighth shaft (TM8) and the ninth shaft (TM9) is arranged to rotate, by means of any of brakes (B1, B2, B3), at least one of the rotary elements of the non-rotary element first, second, third and fourth planetary gear sets (PG1, PG2, PG3, PG4) to be selectively connected to a transmission case (H). Planetary gear train according to Claim 15 wherein by means of any one of couplings (C1, C2, C3) respectively the sixth wave (TM6) with the second wave (TM2), the first wave (TM1) with the fifth wave (TM5) and the first wave (TM1) with the third shaft (TM3) are connected to each other, and wherein the seventh shaft (TM7) with the third rotary element (N3), the seventh rotary element (N7) and the tenth rotary element (N10) is connected, the eighth wave (TM8) with the second Rotating element (N2) and the fourth rotary element (N4) is connected, and the ninth wave (TM9) with the twelfth rotary element (N12) is connected. Planetary gear train according to Claim 16 wherein the clutches (C1, C2, C3) comprise: a first clutch (C1) disposed between the sixth shaft (TM6) and the second shaft (TM2); a second clutch (C2) disposed between the first shaft (TM1) and the fifth shaft (TM5), a third clutch (C3) disposed between the first shaft (TM1) and the third shaft (TM3), and wherein the brakes (B1, B2, B3) a first brake (B1) disposed between the eighth shaft (TM8) and the transmission case (H), a second brake (B2) disposed between the seventh shaft (TM7) and the transmission case (H), and a third brake (B3) disposed between the ninth shaft (TM9) and the transmission case (H). Planetary gear train according to Claim 15 wherein by means of any one of couplings (C1, C2, C3) respectively the sixth wave (TM6) with the fourth wave (TM4), the first wave (TM1) with the fifth wave (TM5) and the first wave (TM1) with the third shaft (TM3) are connected to each other, and wherein the seventh shaft (TM7) with the third rotary element (N3), the seventh rotary element (N7) and the tenth rotary element (N10) is connected, the eighth wave (TM8) with the second Rotating element (N2) and the fourth rotary element (N4) is connected, and the ninth wave (TM9) with the twelfth rotary element (N12) is connected. Planetary gear train according to Claim 18 wherein the clutches (C1, C2, C3) comprise: a first clutch (C1) disposed between the sixth shaft (TM6) and the fourth shaft (TM4); a second clutch (C2) disposed between the first shaft (TM1) and the fifth shaft (TM5), a third clutch (C3) disposed between the first shaft (TM1) and the third shaft (TM3), and wherein the brakes (B1, B2, B3) a first brake (B1) disposed between the eighth shaft (TM8) and the transmission case (H), a second brake (B2) disposed between the seventh shaft (TM7) and the transmission case (H), and a third brake (B3) disposed between the ninth shaft (TM9) and the transmission case (H). Planetary gear train according to any one of Claims 15 to 19 wherein the first, second and third rotary members (N1, N2, N3) are respectively associated with a first sun gear (S1), a first planet carrier (PC1) and a first ring gear (R1), the fourth, the fifth and the sixth Rotary element (N4, N5, N6) respectively associated with a second sun gear (S2), a second planet carrier (PC2) and a second ring gear (R2), the seventh, the eighth and the ninth rotary element (N7, N8, N9) respectively assigned a third sun gear (S3), a third planet carrier (PC3) and a third ring gear (R3), the tenth, eleventh and twelfth rotational elements (N10, N11, N12) are respectively associated with a fourth sun gear (S4), a fourth planet carrier (PC4) and a fourth ring gear (R4), and the thirteenth, fourteenth and fifteenth rotational elements (N13, N14, N15) are respectively associated with a fifth sun gear (S5), a fifth planet carrier (PC5) and a fifth ring gear (R5 ) are.

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